Builder motion for roving frame



May 2, 1967 R. C. MASON ETAL BUILDER MOTION FOR ROVING FRAME Filed NOV. 9, 1964 2 Sheets-Sheet 1 RONALD C. MASON 8 WILLIAM B. STRZELEWIGZ, Jr. BY

their ATTORNEYS May 2, 1967 R.

c. MASON ETAL 3,316,700

BUILDER MOTION FOR ROVING FRAME Filed Nov. 9, 1964 2 Sheets-Sheet 2 L CONTROL VOLTAGE 64 BUILDER SECT.I CLOSED BY RAIL BUILDER 62 swlT movemsm DOWNWARD AT LATCHING RELAY BOTTOM OF RAIL TRAVEL 5 76 @lRELAY COIL) 74 L -77 21 I SECT. 2 I RESET COIL) 0: LR-L 78 I 4 SE01. 2 LAST TO BE Era-3 LR-4 AQJILDER RELAY GR TRIPPED CLOSED BY w RAIL MOVEMENT UPWARD AT TOP L TRAVEL 5O)\IINDEXING SOLENOID NOR-I "7 I 0 DC POWER SUPPLY I I 1 O I v F/@ 3 I20- RAIL UP CLUTCH II8 |L I07 II LR-.|

RAIL DOWN CLUTCH NOTE: LR-2 LATCHING RELAY AS (A) RESET COI (B) RAIL TRAV SHOWN INDICATES L (LR-L) LAST TO BE ENERGIZED ELING DOWNWARD INVENTORS.

RONALD C. MASON 8| IV VJLLIAM B. STRZELEWICZ, Jr.

their ATTORNEYS United States Patent ABSTRACT OF THE DESCLG'SURE A roving frame having bobbins and fliers, cone pulleys connected by a belt, a belt shipper for moving the belt axially of the pulleys, an air cylinder, ratchet, and rack for moving the shipper, and counterrotating electrically-operated clutch means for reciprocating the bobbins.

This invention relates to frames for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin.

The disclosure herein, though not the claimed invention, is substantially the same as disclosures in a copending commonly-assigned application Ser. No. 409,899 by Frederick A. Willis, Jr., for Electric Control Circuit filed concurrently herewith and a copending commonlyassigned application Ser. No. 409,916 by Ronald C. Mason, William B. Strzelewicz, Jr., and Frederick A. Willis, Jr., for Winding Apparatus with Electric Control Circuit also filed concurrently herewith.

Conventional frames for paying off a filamentary materiai from a feed mechanism such as a roving frame and winding the material onto a bobbin to form a package of the material on the bobbin are disclosed in, for example, a patent to Hendrickson No. 2,003,362, assigned to the assignee of the present application. Such machines marked a considerable advance in the art at the time of their introduction, but further improvement of them is desirable.

For example, the conventional design gives rise to a harsh, noisy action of the contact shaft, which must be suddenly geared into a high-speed rotating shaft (the top cone shaft) and suddenly stopped after only half a revolution with much noise and shock to the skip gear, contact dogs, builder nuts, and contact shaft.

Further, conventional apparatus is subject to rail run overs because of the period of no drive when the twin bevel gears are being shifted.

Also, the front roll speed of the conventional frame must be limited to about 300 rotations per minute, because the skip gear does not mesh properly with the top cone bevel gear at speeds greater than that.

Finally, conventional machines may not be stopped safely from an operational point of view at all positions of rail travel.

An object of the present invention is to remedy the shortcomings of the conventional apparatus pointed out above.

In particular, an object of the present invention is to employ the cushioning effect of a compressible fluid in moving the cone-pulley-belt guide, in order to minimize noise and shock.

A further object of the invention is to provide for positive holding of the rail during rail reversal t0 eliminate the period of no drive during rail reversal.

Another object of the invention is to provide a builder mechanism which operates independently of frame speed, thereby permitting front roll speeds substantially in excess of 300 rotations per minute.

Another object of the invention is to provide a frame which can be stopped safely from an operational point of view in any position of rail travel.

These and other objects of the invention are accomplished by providing, in a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin and control means for limiting at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v, and l respectively. The control means preferably comprises a pneumatic piston-cylinder assembly, means for actuating the piston-cylinder assembly at intervals to produce an output, and means coupling the output to the drive means to alter at least one value limited by the control means.

An understanding of further particulars of the invention may be gained from a consideration of the following detailed description of a representative embodiment thereof taken in conjunction with the accompanying figures in the drawings, of which:

FIG. 1 is a fragmentary, sectioned view of one form of accordance with the invention;

FIG. 2 is an enlarged perspective view of a portion of the apparatus of FIG. 1; and

FIG. 3 is a schematic diagram of an electric circuit constituting .one of a number of possible means adapted to instrument the apparatus of the present invention.

FIG. 1 shows drive means 10 connected by suitable linkages H, 12 to a top cone pulley i4 and a flier 16, respectively, to rotate the top cone pulley 14 at constant speed and the flier at constant speed.

The top cone pulley M is connected to a bottom cone pulley 18 by a cone pulley belt 20 extending therebetween and tightly drawn thereabout so that the rotation of the top cone pulley 14 in the direction indicated by the arrow associated with the top cone pulley 14 is effective to rotate the bottom cone pulley 13 in the direction indicated by the arrow associated with the bottom cone pulley 18.

The top cone pulley 14 is tapered, either linearly as shown or non-linearly, so that its diameter perpendicular to its axis of rotation adjacent to its base 22 (the conefrustum base to the left as seen in the figure) is larger than the corresponding diameter adjacent to its base 24. Similarly, the bottom cone pulley 18 is tapered, either linearly as shown or non-linearly, and has a large base 26 and a small base 27. The bottom cone pulley is arranged, however, with its large base 26 to the right of its small base 27 as seen in the figure rather than to the left.

A cone-pulley-belt guide or shipper 28 envelops a por tion of the belt 20 to guide the belt 20 and move it longitudinally of the axes of the upper and lower cone pulleys 14, 18. Those skilled in the art will readily understand that the cone pulleys 14, 13 and the belt 20 constitute a variable-mechanical-advantage means and that, for example, when the belt 20 is moved to the left as indicated in FIG. 1, the rotational speed of the lower cone pulley 18 increases and that, when the belt 20 is moved to the right as seen in FIG. 1, the rotational speed of the lower cone pulley 18 decreases.

In the winding of roving, for example, it is normally desired to shift the belt towards the right as seen in FIG. 1 following each traverse with respect to each other of the flier l6 and a bobbin 3% on which the roving is to be wound. The flier 16 is made to rotate, as noted partly-schematic, partlyapparatus constructed in above, by the drive means at a constant speed. The bobbin 30, being connected to the lower cone pulley 18 by suitable linkages 32, 33, rotates in the same direction in which the flier 16 rotates but more rapidly than the flier 16. The feed mechanism and bobbin thus rotate with respect to each other at a rotational velocity w. As the thickness of the package of roving increases, the tangential speed of the package would become excessively great, except for the fact that the rotational speed of the bobbin 30 decreases with each successive traverse as the belt 20 moves to the right as seen in FIG. 1. Also, in order to provide the tapered bobbin shape indicated at t, the length of each successive traverse is preferably decreased.

The belt shipper 28 has formed thereon a rack 34 adapted to be driven by gearing 36 which is in turn actuated by a ratchet 38 under the control of a piston rod 40 of a piston-cylinder assembly 42.

Thus, movement of the piston 43 (FIG. 2) of the piston-cylinder assembly 42 to, for example, the right as seen in FIG. 1 and in the direction of the lower arrow in FIG. 2, actuates the gearing mechanism 36 through the ratchet assembly 38 to move the rack 34 and hence the shipper 28 to the right as seen in FIG. 1 and therefore shift the belt 20 to the right and change the mechanical advantage of the variable-mechanicaladvantage means constituted by the cone pulleys 14, 18 and the belt 20. The directions of rotation of the gears constituting the gearing mechanism 36 are shown by appropriate arrows in FIG. 2. Movement of the piston 43 in the opposite directioni.e., to the left as seen in FIG. lhas no effect on the location of the belt 20 longitudinally of the axes of the cone pulley 14, 18, inasmuch as the ratchet 38 is free wheeling in response to such movement of the piston 43.

The piston 43 of the piston-cylinder assembly 42 is actuated by an air supply line 44 and an air exhaust line 46 communicating with a shiftable valve 48 under the control of a solenoid 50 and spring 54. The valve 48 moves to the position shown in response to energization of the solenoid 50. In the position of the valve shown, the air supply line 44 communicates through a passage 45 in the valve 48 with a line 52 for moving the piston 43 of the piston-cylinder assembly 42 to the right as seen in FIG. 1 and performing an indexing function-Le, shifting the cone guide 28. A line 58 communicating with a passage 47 in the valve 48 permits the exhaust of air from the right-hand end of the cylinder to the exhaust line 46. With the valve 48 shifted to the left under the influence of the spring 54, the solenoid 50 being tie-energized, the air supply line 44 is connected through a passage 56 in the valve 48 with the line 58 to the right-hand end of the pistoncylinder assembly 42 to drive the piston of the pistoncylinder assembly to the left as seen in FIG. 1. In this position, the left-hand end of the piston-cylinder assembly 42 is connected to a passage 60 in the valve 48 to permit exhaust of air in the left-hand end of the piston-cylinder assembly 42 through the exhaust line 46.

Flow-control valves 61, 61' (FIG. 2) control the speed of the piston 43 and prevent shock loads.

An air pressure switch 63 stops the frame from operating if the air pressure in the mill falls below a safe builder operating pressure-usually about 40 pounds per square inch.

The solenoid 50 is shown also in FIG. 3. As that figure shows, the indexing solenoid 50 is energized when 1 contacts CR-1 are closed, inasmuch as the contacts CR-l and solenoid 50 are in series between lines 62, 64, across which a DC. control voltage is applied.

The contacts CR-l are in turn closed when a builder relay CR is energized. Provision may be made to energize the builder relay at either end of the relative traverse of the feed mechanism or flier 16 and bobbin 30 with respe'ct to each other, but provision is preferably made for energizing the builder relay CR at each end of the relative traverse of the feed mechanism 16 and the bobbin 30 with respect to each other. To this end, the builder relay CR is connected by a pair of normally-open contacts LR-3 to a line 66 and by a pair of normallyclosed contacts LR-4 to a line 68.

The lines 66 and 68 extend between the control-voltage leads 62 and 64 and therefore provide means for energizing the relay coil LR-R and reset coil LR-L, respectively, of a building latching relay 74. The relay coil LR-R of the latching relay 74 is energized upon closing of a first section 76 of a builder switch 77, and the reset coil LR-L is energized upon closing of a second section 78 of the builder switch 77.

The first and second sections 76 and 78 of the builder switch 77 are in turn closed at opposite ends of the relative traverse of the flier 16 and bobbin 30 with respect to each other by contact of first and second contact dogs 80 and 82 with a third contact dog 84 (FIG. 1). The contact dogs 80 and 82 are mounted on builder nuts 86 and 88, respectively, which are in turn threadedly engaged with a rotatable screw 90 having a lower portion 92 threaded oppositely to an upper portion 94 and a topmost portion 90 square in cross section so as to be rotatable by a gear train 130. The nuts 86, 88, screw 90, and contact dogs 80, 82 are mounted on support means 96 rigidly retained on a bobbin rail 98 on which is also mounted the bobbin 30. The bobbin rail 98 is made to reciprocate upwardly and downwardly, so that a relative traverse of length l and at velocity v of the feed mechanism or flier 16 and bobbin 30 with respect to each other is established. The means for establishing the relative traverse includes a rail lifter 100 having thereon a rack 101 engaged with a train of gears 102 connected to a shaft 104. The shaft 104 in turn is driven through -a reversible clutch mechanism 105 having clutches 106, 107 which are driven respectively by a pair of bevel gears 110, 114. The gears 110 and 114 rotate in opposite directions with respect to each other, inasmuch as they are coaxial and are driven by a bevel gear 112 in constant engagement with the gears 110, 114 and having its axis normal to the axes of the gears 110, 114.

As noted above, the gear train 32 is driven by the lower cone pulley 18 at a speed depending on the location of the belt 20. Inasmuch as the lower cone pulley 18 always turns in the same direction, the gear train 32 and the bevel gears 108, 112 also always turn in the same direction.

Depending on which of the clutches 106, 107 is coupled to the shaft 104 (the other clutch being disengaged from the shaft 104 and free wheeling), the shaft 104 turns in one direction or the other and, through the gear train 102 and the rack 101 and lifter element 100, reciprocates the bobbin rail 98 and the bobbin 30 upwardly and downwardly. For example, as shown in FIG. 1, energization of the clutch 106 causes the bobbin rail 98 to move downwardly and energization of the clutch 107 causes the rail 98 to move upwardly.

A brake 116 is provided for immobilizing the shaft 104 and hence the bobbin 98 in the event of failure of both clutches, such as might occur during power failure. During normal operation, the brake 116 is electrically held open; under power-off conditions, the brake is spring set.

The clutches 106 and 107 are preferably electrically operated by the circuit shown in FIG. 3. The clutch 107 is energized to cause the bobbin rail 98 to move upwardly when normally-open contacts LR-l are closed between D.C. leads 118 and 120. Similarly, the rail-down clutch 106 is energized to move the rail 98 downwardly when the normally-closed contacts LR-2 are closed between the same two leads 118 and 120. The currentdelay characteristics inherent in the electric reversing clutches insure adequate holding power during rail reversal. Thus, rail run overs are eliminated.

All of the contacts LR-l, LR-2, LR-3, and LR-4 are under the control of the builder latching relay 74. The coils LR-R and LR-L of the latching relay 74 are adapted to be alternately energized, and the latching relay 74 is constructed in such a manner that, regardless of whether the relay coil LRR or the reset coil LRL is energized, all four of the contacts LR-l, LR2, LR3, and LR4 are reversed and remain in their new states until energization of the other of the coils LRR and LRL. To this end, the contacts LR-1, LR-2, LR-3, and LR-4 are directly attracted by the electromagnet of the relay coil LR- R. Energization of the coil LRR therefore magnetically moves the contacts LR-1, LR2, LR3, and LR4 to their magnetically-caused states, in which states they are mechanically held by mechanical holding means represented at 121, regardless of whether the relay coil LR-R remains energized. The electromagnet of the reset coil LRL does not act directly on the contacts LR-l, LR2, LR3, and LR4 but acts, instead, on the mechanical holding means 121 to release the mechanical holding means 121 and permit the contacts LR-ll, LR2, LR3, and LR- 4 to return to their normal or mechanically-caused states shown in FIG. 3. The holding means 121 provides a memory to prevent the rail 98 from going in the Wrong direction on start-up after the frame has been stopped for any reason.

Inasmuch as there are five pairs of contacts LRI, LR- 2, LR3, and LR4, and (IR-1, each adapted to occupy alternately either of two states, there are ten different contact states which need to be separately identified. Also, there are four different times which need to be considered in a traverse cycle: time t during which the coil LRR is energized and the coil LRL is de-energized; time t during which both coils LRR and LRL are de-ener 'gized; time 13, during which the coil LRL is energized and the coil LRR is deenergized; and time 1 during which bothooils LRR and LRL are de-energized. Times t and t are of substantially equal duration and times t and L; are of duration substantially equal to each other and substantially exceeding the duration of times t and 2 Finally, it is to be noted that the contacts LRI in their closed state facilitate the performance of a first function such as energizing the rail-up clutch 187 to cause the rail 98 to move upwardly; the contacts LR2 in their closed state facilitate the performance of a second function such as energizing the rail-down clutch 106 to cause the rail 98 to move downwardly; and the contacts CR-l in their closed state facilitate the performance of a third function such as energization of the solenoid 50 to index the guide or shipper 28.

The operation of the apparatus of the invention will now be readily understood by those skilled in the art. FIG. 3 illustrates the case where the reset coil LRL was the last to be energized, so that all contacts LR-l, LR2, LR3, and LR-4 are shown in their normal or mechanically-caused states. Thus, the contacts LR2 are closed, energizing the rail-down clutch 106 and causing the bobbin 30 to move downwardly with respect to the flier 16. At the bottom of the traverse, the contact dogs 82 and 84 (FIG. 1) engage each other, closing the switch 76 shown in FIG. 3. This closing of the switch 76 energizes the relay coil LRR and reverses all of the contacts LR-l, LR Z, LR3, and LR 4. The contacts LR-l are therefore closed, energizing the rail-up clutch, and contacts LR2 are open, de-energizing the rail-down clutch, so that the rail begins to move up. The delay characteristic referred to above eliminates run over of the rail 98 during the reversal of traverse motion. At the same time, the contacts LR-3 close, completing a circuit through the switch 76, the contacts LR3, and the builder relay CR. This causes the contacts CR1 under the control of the builder relay to close, indexing the indexing solenoid 50. The indexing of the solenoid 5t) shifts the piston of the piston-cylinder assembly 42 in the manner noted above to move the cone guide belt shipper 28 to the right through the gear train 36, as shown in FIG. 1.

A gear train 130 is actuated by movement of the rack 34 to turn the rod 90 and bring the nuts 86 and 88 closer together to shorten the succeeding traverse. The length l of a given traverse is of course a function of the distance x between the contact dogs 88 and 82.

When the rail-up clutch 106 has caused the rail 98 to move upwardly sufiiciently to disengage the contact dogs 82 and 84 from each other, the switch 76 is opened, so that the relay coil LRR is de-energized. Because the relay coil 74 is a latching relay the contacts LRL LR2, LR3, and LR4 remain in their magneticallycaused states even though the relay coil LRR is deenergized. The opening of the switch 76 breaks the circuit through the now-closed contacts LR3 and the builder relay CR, however, so that the relay CR is deenergized, the contacts CR-l open, and the indexing solenoid 50 returns to its normal position under the urging of the spring 54 (it is to be noted that FIG. 1 shows the valve 48 in its indexing rather than in its normal position). When the valve 4-8 returns to its normal position, the ratchet 38 free-wheels and does not move the guide or shipper 28 to the left; the shipper accordingly remains in its new position.

At the upper end of the traverse, the contact dogs and 8d make contact with each other, closing the switch 78 and energizing the reset coil LRL of the building latching relay 74. This causes reversal of all contacts LRI, LR2, LR3, and LR4 to their normal positions as shown in FIG. 3 and energizes the rail-down clutch 106 to cause the rail 98 to move downwardly, while again avoiding rail run over. Also, the closing of the switch 78 actuates the builder relay CR through the contacts LR4, closes the contacts LRI, and indexes the indexing solenoid 58 as noted above. When the rail has moved downwardly sufliciently to separate the contact dogs 80 and 84, the switch 78 is opened, thereby de-energizing the reset coil LRL. Inasmuch, however, as the relay is a latching relay and all contacts are in their normal or mechanically-caused states, the contacts LR-l, LR2, LR3, and LR4 remain in their new states, even though the reset coil LRL is deenergized. The opening of the switch 78 also breaks the circuit through the contacts LR-4 and the builder relay CR, so that the relay CR is de-energized, the contacts CR-ll open, and the indexing solenoid 50 returns to its normal position under the urging of the spring 54. The ratchet 38 again free-wheels, so that the shipper 28 remains in its new position.

A wind-back motor 14a is connected through gearing 142, a clutch 144, and a shaft and pinion 146 forming a portion of the gear train 36 to the rack 34 to return the guide 28 and builder nuts 86, 88 to their starting positions at the end of the package-building operation. The clutch 144 is keyed to a shaft 145 by a keyway 148 but movable axially along the shaft by clutch-control means 150. The clutch 144 is disengaged during the building operation and engaged at the end thereof to eliminate the need for manual rewinding.

The present invention relates only to the subject matter of FIGS. 1 and 2, combined as necessary with broadlyrecited means for instrumenting it. It does not relate to the details of FIG. 3, which is a separate invention by Frederick A. Willis, Jr., and which is disclosed in the present application merely as one means of instrumenting the apparatus of the present invention. Obviously, the apparatus of the present invention could be instrumented in other ways. Nor does the present invention relate to the details of the subject matter of FIGS. 1 and 2 in combination with the details of the subject matter of FIG. 3, which is a separate invention by Ronald C. Mason, William B. Strzelewicz, Jr., and Frederick A. Willis, Jr.

Thus, there is provided in accordance with the invention novel and highly-effective means for paying ofi a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin. The use of a pneumatic pistoncylinder assembly eliminates the harsh, noisy action of the contact shaft and the shock to the skip gear, contact dogs, builder nuts, and contact shaft. The reversing clutches eliminate rail run overs during reversal of rail movement by always maintaining positive holding of the rail. The front roll speed may be varied independently of frame speed and may be substantially in excess of 300 rotations per minute, thereby facilitating greater manufacturing efficiency. Further, the machine may be stopped safely in any position of rail travel. Many alternative embodiments within the scope of the invention will readily occur to those skilled in the art. Accordingly, the invention is to be construed as including all of the modifications thereof which fall within the scope of the appended claims.

We claim:

1. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v, and 1, respectively, the control means comprising a pneumatic piston-cylinder assembly, means for actuating the pistoncylinder assembly at intervals to produce an output, and means coupling the output to the drive means to alter at least one value limited by the control means.

2. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the traverse length to a value I, the control means including (a) first and second contact means spaced apart from each other a distance x of which the value I is a function, (b) third contact means adapted to engage alternately the first and second contact means at opposite ends of the traverse, (c) first reversing means responsive to engagement of the first and third contact means for reversing the direction of the traverse from a first direction to a second direction, (d) second reversing means responsive to engagement of the second and third contact means for reversing the direction of the traverse from the second direction to the first direction, (e) a pneumatic piston-cylinder assembly responsive to at least one of the engagement of the first and third contact means with each other and the engagement of the second and third contact means with each other to produce an output, and (f) means coupling the output to the first and second contact means to alter the distance x and hence the value I.

3. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (a) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (b) variablemechanical-advantage means, and control means for (l) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w, the control means including (a) varying means for varying the mechanical advantage of the variable-mechanical-advantage means, (b) a pneumatic piston-cylinder assembly, (c) means for actuating the piston-cylinder assembly at intervals to produce an output, and ((1) means coupling the output to the varying means to vary the mechanical advantage of the variable-mechanical-advantage means and alter the value w.

4. In a frame for paying off a filamentary material from -a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (a) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (b) variable-mechanical-advantage means, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w and the traverse length to a value I, the control means including (a) first and second contact means spaced apart from each other a distance x of which the value I is a function, (h) third contact means adapted to engage alternately the first and second contact means at opposite ends of the traverse, (c) first reversing means responsive to engagement of the first and third contact means for reversing the direction of the traverse from a first direction to a second direction, (d) second reversing means responsive to engagement of the second and third contact means for reversing the direction of the traverse from the second direction to the first direction, (e) varying means adapted to vary the mechanical advantage of the variable-mechanical-advantage means, (f) indexing means including a piston-cylinder assembly responsive to at least one of the engagement of the first and third contact means with each other and the engagement of the second and third contact means with each other to produce an output, and (g) means coupling the output (1) to the varying means to vary the mechanical advantage of the variable-mechanical-advantage means and alter the value w and (ii) to the first and second contact means to alter the distance x and hence the value I.

5. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (a) a pair of counterrotating clutch means and rotatable shaft means alternately engagea-ble by the clutch means and (b) variable-mechanical-advantage means having at least one cone pulley and a belt, there being a driving relation therebetween, and control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w and the traverse length to a value I, the control means including (a) first and second contact means spaced apart from each other a distance x of which I is a function, (b) third contact means adapted to engage alternately the first and second contact means at opposite ends of the traverse, (c) first reversing means responsive to engagement of the first and third contact means for reversing the direction of the traverse from a first direction to a second direction, (d) second reversing means responsive to engagement of the second and third contact means for reversing the direction of the traverse from the second direction to the first direction, (e) guide means adapted to shift the belt longitudinally of the cone pulley to vary the mechanical advantage of the variable-mechanicaladvantage means and hence the value w, (f) indexing means including a piston-cylinder assembly responsive to at least one of the engagement of the first and third con-tact means with each other and the engagement of the second and third contact means with each other to produce an output, and (g) means coupling the output (i) to the guide means to actuate the guide means to shift the belt longitudinally of the cone pulley to alter the mechanical advantage of the variable-mechanical advantage means and hence the value w and (ii) to the first and second contact means to alter the distance x and hence the value I.

6. In a frame fOr paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bob-bin, the improvement comprising (a) drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including (i) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (ii) variablemechanical-advantage means having at least one cone pulley and a belt, there being a driving relation therebetween, and (b) control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w and the traverse length to a value I, the control means including (i) first and second contact dog means spaced apart from each other a distance x of which I is a function, (ii) third contact dog means adapted to engage alternately the first and second contact dog means at opposite ends of the traverse, (iii) first reversing means responsive to engagement of the first and third contact means for reversing the direction of the traverse from a first direction to a second direction, (iv) second reversing means responsive to engagement of the second and third contact means for reversing the direction of the traverse from the second direction to the first direction, (v) guide means adapted to shift the belt longitudinally of the cone pulley to vary the mechanical advantage of the variable-mechanical-advantage means and hence the value w, (vi) a pneumatic piston-cylinder assembly responsive to at least one of the engagement of the first and third contact means and the engagement of the second and third contact means to produce an output, and (vii) means coupling the output (1) to the guide means to actuate the guide means to shift the belt longitudinally of the cone pulley to alter the mechanical advantage of the variable-mechanical-advantage means and hence the value w and (2) to the first and second contact dog means to alter the distance x and hence the value I.

7. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising (a) drive means for establishing a relative rotation of the feed mechanism and bobbin With respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other having a component longitudinal of the axis of rotation of the bobbin, the drive means including (i) a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means and (ii) variable-mechanical-advantage means, and (b) control means for (1) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting the rotational velocity to a value w, the traverse length to a value I, and the traverse velocity to a value v, the control means including (i) first and second contact means spaced apart from each other a distance x of which I is a function, (ii) third contact means adapted to engage alternately the first and second contact means at opposite ends of the traverse, (iii) first reversing means responsive to engagement of the first and third contact means for reversing the direction of the traverse from a first direction to a second direction, (iv) second reversing means responsive to engagement of the secono and third contact means for reversing the direction of the traverse from the second direction to the first direction, (v) varying means adapted to vary the mechanical advantage of the variable-mechanical-advantage means, (vi) indexing means including a piston-cylinder assembly responsive to at least one of the engagement of the first and third contact means with each other and the engagement of the second and with each other to produce an output, and (vii) means coupling the output (1) to the varying means to vary the mechanical advantage of the variable-mechanicaladvantage means and alter the values w and v and (2) to the first and second contact means to alter the distance x and hence the value I.

8. In a frame for paying ofi. a filamentary material from a feed mechanism and Winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin With respect to each other longitudinally of the axis of rotation of the bobbin, control means adapted to modify its condition to limit at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v and 1, respectively, motor means adapted to restore the control means to its original condition, and clutch means for selectively engaging the motor means to the control means to restore the control means to its original condition.

9. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative tnaverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, and control means for alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other, the control means including a piston-cylinder assembly adapted to produce an output, and means coupling the output to the drive means to modify the action of the drive means.

10. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, control means for (l) alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other and (2) limiting at least one rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v and l, respectively, the control means comprising a pneumatic piston-cylinder assembly, means for actuating the piston-cylinder assembly at intervals to produce an output, means coupling the output to the drive means to alter at least one value limited by the control means, and flow control means connected to the piston-cylinder assembly to regulate the speed of operation of the piston-cylinder assembly.

11. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for establishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, control means for limiting at least one of (a) the rotational velocity, (b) the traverse velocity, and (c) the traverse length to values w, v and I, respectively, the control means comprising a pneumatic piston-cylinder assembly, means for actuating the piston-cylinder assembly at intervals to produce an output, means coupling the output to the drive means to alter at least one value limited by the control means, and pressure-responsive means connected to the pneumatic piston-cylinder assembly for preventing operation of the frame in the of (a) the event that pneumatic pressure to the pneumatic pistoncylinder assembly falls below a prescribed value.

12. In a frame for paying off a filamentary material from a feed mechanism and winding the material onto a bobbin to form a package of the material on the bobbin, the improvement comprising drive means for est-ablishing a relative rotation of the feed mechanism and bobbin with respect to each other and a relative traverse of the feed mechanism and bobbin with respect to each other longitudinally of the axis of rotation of the bobbin, the drive means including a pair of counterrotating clutch means and rotatable shaft means alternately engageable by the clutch means, control means for alternately energizing the clutch means to cause said relative traverse alternately to assume first and second directions opposite to each other, and brake means for preventing rotation of the rotatable shaft means in the event of simultaneous failure of both counterrotating clutch means to engage the rotatable shaft means.

References Cited by the Examiner UNITED STATES PATENTS 3,015,203 1/1962 Heiberg 5798 X 3,203,163 8/1965 Long 5798 3,287,891 11/ 1966 Pfeifer 57-99 FRANK J. COHEN, Primary Examiner. JOHN PETRAKES, Examiner. 

1. IN A FRAME FOR PAYING OFF A FILAMENTARY MATERIAL FROM A FEED MECHANISM AND WINDING THE MATERIAL ONTO A BOBBIN TO FORM A PACKAGE OF THE MATERIAL ON THE BOBBIN, THE IMPROVEMENT COMPRISING DRIVEN MEANS FOR ESTABLISHING A RELATIVE ROTATION OF THE FEED MECHANISM AND BOBBIN WITH RESPECT TO EACH OTHER AND A RELATIVE TRAVERSE OF THE FEED MECHANISM AND BOBBIN WITH RESPECT TO EACH OTHER LONGITUDINALLY OF THE AXIS OF ROTATION OF THE BOBBIN, THE DRIVE MEANS INCLUDING A PAIR OF COUNTERROTATING CLUTCH MEANS AND ROTATABLE SHAFT MEANS ALTERNATELY ENGAGEABLE BY THE CLUTCH MEANS, AND CONTROL MEANS FOR (1) ALTERNATELY ENERGIZING THE CLUTCH MEANS TO CAUSE SAID RELATIVE TRAVERSE ALTERNATELY TO ASSUME FIRST AND SECOND DIRECTIONS OPPOSITE TO EACH OTHER AND (2) LIMITING AT LEAST ONE OF (A) THE ROTATIONAL VELOCITY, (B) THE TRAVERSE VELOCITY, AND (C) THE TRAVERSE LENGTH TO VALUES W,V AND L, RESPECTIVELY, THE CONTROL MEANS COMPRISING A PNEUMATIC PISTON-CYLINDER ASSEMBLY, MEANS FOR ACTUATING THE PISTONCYLINDER ASSEMBLY AT INTERVALS TO PRODUCE AN OUTPUT, AND MEANS COUPLING THE OUTPUT TO THE DRIVE MEANS TO ALTER AT LEAST ONE VALUE LIMITED BY THE CONTROL MEANS. 